KR20040073544A - Scroll-type compressor - Google Patents

Abstract

In the revolving angle region where the rollover moment acting on the movable scroll 26 becomes more than a predetermined value during the idle scroll 26, by forming an adjusting mechanism 56 for generating the rollover prevention moment which reduces the rollover moment. The negative pressure of the movable scroll 26 with respect to the fixed scroll 22 corresponds to the fluctuation of the overturning moment caused by the revolution of the movable scroll 26, thereby stabilizing the idle operation of the movable scroll 26, thereby providing a scroll compressor ( Increase the compression efficiency of 1).

Description

Scroll Compressor {SCROLL-TYPE COMPRESSOR}

BACKGROUND ART Conventionally, for example, a scroll compressor is used as a compressor for compressing refrigerant gas in a refrigeration cycle. The scroll compressor includes a fixed scroll and a movable scroll having a spiral wrap engaged with each other in the casing. The fixed scroll is fixed to the casing, and the movable scroll is connected to the eccentric portion of the drive shaft (crankshaft). In this scroll type compressor, the movable scroll only rotates without rotating against the fixed scroll, thereby contracting the compression chamber formed between the laps of both scrolls, thereby compressing a gas such as a refrigerant.

In the scroll compressor, as shown in Fig. 10, a structure is adopted in which the movable scroll OS is pushed in the axial direction with respect to the fixed scroll FS. This overturning moment is generated when the so-called overturning moment occurs due to the axial gas load Fz acting on the movable scroll OS by the gas compression operation and the radial load Fx that is the combined force of the gas force and the centrifugal force. When the movable scroll OS is inclined (overturned), since the refrigerant leaks and the efficiency is lowered, it is an object to prevent the occurrence of such a phenomenon.

It is known that the axial gas load Fz and the radial load Fx reach peaks at about the same time as shown in FIG. 11. Specifically, these loads Fz and Fx become maximum at the crank angle (revolution angle of the movable scroll OS) at which the compression chamber internal pressure reaches a maximum value, and the tipping moment M is also maximized at this time. .

Challenge

Therefore, in order to reliably prevent the rollover of the movable scroll OS during the compressor operation, it is necessary to set the magnitude of the negative pressure on the basis of the maximum value of the rollover moment. However, if this negative pressure is simply set to a value such that the movable scroll (OS) does not overturn when the overturning moment is maximum, the underpressure becomes excessively strong at the crank angle at which the overturning moment is smaller than this, resulting in high efficiency due to mechanical loss. There is a risk of deterioration.

On the other hand, in the scroll type compressor, a high pressure refrigeration oil is supplied to the sliding surfaces of the fixed scroll (FS) and the movable scroll (OS) to push the movable scroll (OS) with a force represented by Fo against the negative pressure. There is one adopted. For example, Japanese Patent Application Laid-Open No. 2001-214872 describes a structure for adjusting negative pressure in response to a change in compression ratio (or high and low differential pressure) caused by a change in device operating conditions. However, even in this compressor, the pressing-back force is not adjusted in response to the fluctuation of the axial gas load or the overturning moment during the idle scroll OS. That is, in this compressor, the generation / stop of the pushing force is simply switched according to the magnitude of the compression ratio (or high and low differential pressure), and when the pushing force is generated, the pushing force is almost constant regardless of the crank angle. For this reason, the compressor cannot cope with fluctuations of the rollover moment during idle scroll (OS) idle, etc., and it has not been able to sufficiently stabilize the idle motion of the movable scroll.

The present invention has been devised in view of the above problems, and an object thereof is that the negative pressure of the movable scroll with respect to the fixed scroll corresponds to the axial gas load or the rollover moment variation associated with the movable scroll revolution. It is to stabilize the idle operation and further improve the compression efficiency of the scroll compressor.

BACKGROUND OF THE INVENTION 1. Field of the Invention The present invention relates to a scroll compressor, and more particularly, to a scroll compressor having a mechanism for adjusting the pressing force in a configuration for pushing the movable scroll to the fixed scroll and preventing the movable scroll from tipping over. will be.

BRIEF DESCRIPTION OF THE DRAWINGS Sectional drawing which shows the whole structure of the scroll compressor which concerns on 1st Example of this invention.

2 is a plan view of the movable scroll of the first embodiment;

3 is a plan view of the movable scroll of the second embodiment;

Figure 4 is a plan view of the movable scroll of the third embodiment.

Fig. 5 is a sectional view of the fixed scroll and movable scroll of the fourth embodiment.

6 is a positional relationship diagram of the oil groove and the oil introduction passage opening of the fourth embodiment.

Fig. 7 is a characteristic diagram showing variation in the pushing force of the movable scroll by the refrigerant gas of the fourth embodiment.

Fig. 8 is a positional relationship diagram of an oil groove and an oil passage opening in the fifth embodiment.

Fig. 9 is a sectional view of the fixed scroll and movable scroll of the sixth embodiment.

10 is a view showing a force acting on the movable scroll of a conventional scroll compressor.

FIG. 11 is a characteristic diagram showing variation in force and rollover moment acting on a movable scroll of a conventional scroll compressor. FIG.

The present invention is to stabilize the negative pressure by generating a moment acting to reduce or offset the rollover moment, or by changing the pushing force of the movable scroll 26 according to the revolution angle of the movable scroll 26. It is.

First, in the invention described in claims 1 to 7, the overturn prevention moment for reducing the overturn moment at a predetermined crank angle is generated.

Specifically, the invention of claim 1 further comprises a fixed scroll (22) fixed in the casing (10), a movable scroll (26) engaged with the fixed scroll (22), and a movable scroll (26). It is assumed that a scroll compressor is provided with negative pressure means 37b, 52 which are pushed in the axial direction with respect to the pressure direction, and an adjusting mechanism 56 for adjusting the negative pressure of the movable scroll 26 with respect to the fixed scroll 22.

In the scroll compressor, the adjusting mechanism 56 reduces the rollover moment in the rotational angle region at which the rollover moment acting on the movable scroll 26 becomes greater than or equal to a predetermined value during the rotation of the movable scroll 26. And configured to generate an anti-overturning moment.

In the invention according to claim 1, the anti-overturning moment acts on the movable scroll 26 being prone to overturning in the region of the revolving angle in which the overturning moment increases when the movable scroll 26 revolves. Since the overturning moment is reduced by this overturning prevention moment, the movable scroll 26 is less likely to be rolled over in the angular region, thereby enabling stable idle operation.

The invention described in claim 2 is that in the scroll compressor according to claim 1, the adjustment mechanism 56 prevents the rollover in the revolving angle region in which the rollover moment acting on the movable scroll 26 is equal to or larger than a predetermined value. And the moment is configured to act in a direction substantially opposite to the rollover moment.

In the invention according to claim 2, since the anti-overturn moment acts in the direction of eliminating the overturn moment in the revolving angle region where the overturn moment is increased, the overturning of the movable scroll 26 is more difficult to occur, and the revolving operation is further increased. It is stable.

According to the invention of claim 3, in the scroll compressor according to claim 1 or 2, the adjusting mechanism 56 includes an oil groove formed on the sliding surface of the fixed scroll 22 and the movable scroll 26. 55 and the oil introduction passage 53 for introducing the high pressure oil into the oil groove 55, the oil groove 55, the working angle of the high pressure pressure to the movable scroll 26, the idle angle It is characterized in that it is formed to be eccentric from the center of the movable scroll 26 in the region.

In the invention according to claim 3, the action of the pushing force due to the pressure of the high pressure oil introduced into the oil groove 55 is eccentric from the center of the movable scroll 26, so that the rollover prevention moment is generated. Therefore, when the rollover moment becomes more than a predetermined value according to the idle scroll 26, the rollover moment can be reduced by the rollover prevention moment generated by the high pressure oil pressure, so that the idle operation of the movable scroll 26 is stabilized. In the revolving angle region where the rollover moment is smaller than the predetermined value, the strength of the negative pressure may be determined so that the movable scroll 26 is not rolled over in the reverse direction by the rollover prevention moment.

In addition, the invention according to claim 4 specifies the shape of the oil groove 55. The invention of claim 4, wherein the oil groove 55 is formed in an annular shape, and the fixed scroll 22 or the center thereof is eccentric from the center of the movable scroll 26 in the idle angle region. It is characterized in that formed on the movable scroll (26).

The invention of claim 5 is that the oil groove 55 area is formed so as to be smaller than the reaction side in the action side of the tipping moment with respect to the center of the movable scroll 26 in the idle angle region. It features.

The invention according to claim 6 is characterized in that the oil groove 55 has an overturning moment with respect to the center of the movable scroll 26 concentric with the center of the movable scroll 26 and in the revolving angle region. It is characterized in that part 62 of the working side is cut off.

The invention described in claim 7 is characterized in that the oil groove 55 has an overturning moment with respect to the center of the movable scroll 26 concentric with the center of the movable scroll 26 and in the revolving angle region. In response to the side, the groove width is enlarged, characterized in that it has an enlarged width portion (64).

In the invention according to claim 4, the annular oil groove 55 is eccentric from the center of the movable scroll 26, or reacts with the action of the tipping moment with respect to the center of the movable scroll 26, respectively. By changing the area on the side, the rollover prevention moment due to the high pressure oil is generated in the revolving angle region, and the rollover moment is reduced.

Next, in the invention of claims 8 to 13, the pushing force of the movable scroll 26 is reduced or interrupted at a predetermined crank angle.

Specifically, the invention of claim 8, like the invention of claim 1, includes a fixed scroll 22 fixed in the casing 10, a movable scroll 26 engaged with the fixed scroll 22, Negative pressure means (37b, 52) for pushing the movable scroll (26) axially with respect to the fixed scroll (22), and an adjusting mechanism (67) for adjusting the negative pressure of the movable scroll (26) against the fixed scroll (22). Suppose a scroll compressor having a.

In this scroll compressor, the adjustment mechanism 67 generates a force for pushing the movable scroll 26 out of the fixed scroll 22 against the negative pressure, while compressing the gas during idle of the movable scroll 26. It is characterized in that it is configured to block this pushing force in the revolving angle region where the tipping moment acting on the movable scroll 26 becomes equal to or larger than a predetermined value.

In the invention according to claim 8, when the movable scroll 26 revolves to compress gas, the rollover moment acting on the movable scroll 26 varies with the revolution as shown in FIG. When it becomes large in the revolving angle area, the pushing force by the adjustment mechanism 67 is interrupted. Therefore, the force of the axial gas load and the pushing force and the negative pressure by the negative pressure means 37b and 52 can be prevented from becoming below the required minimum negative pressure. Except for this angular region, an excessive negative pressure is also not generated by applying a pushing force to the movable scroll 26. In this way, the movable scroll 26 executes a stable idle operation without overturning or overpressure.

According to the invention of claim 9, in the scroll compressor according to claim 8, the adjustment mechanism (67) includes an oil groove (55) formed on the sliding surface of the fixed scroll (22) and the movable scroll (26), The oil groove 55 and the oil introduction passage 53 which are in communication with the oil groove 55 are provided to introduce the high pressure oil into the oil groove 55, and the oil groove 55 and the oil introduction passage 53 are operated by gas compression. In a revolving angle region in which the rollover moment acting on the scroll 26 becomes equal to or greater than a predetermined value, the communication state is characterized in that it is configured to be blocked. For example, when the oil groove 55 is formed in the fixed scroll 22 and the oil introduction passage 53 is formed in the movable scroll 26, the opening end of the oil introduction passage 53 is movable scroll 26. Since the rotor is orbiting around the circumference having a radius of revolution, the oil groove 55 does not communicate with only a part of the trajectory (the position of the open end when the movable scroll 26 is in the idle angle region). You can make it communicate with outside.

In the invention according to claim 9, a force for pushing the movable scroll 26 to the fixed scroll 22 is generated when the oil introduction passage 53 communicates with the oil groove 55. On the other hand, in the revolving angle region where the rollover moment acting on the movable scroll 26 by gas compression becomes a predetermined value or more, the communication state is interrupted and no pushing force is generated. Therefore, in the region where the tipping moment generated by gas compression is small, the sum of the axial gas load and the pushing force by the high pressure oil and the negative pressure by the negative pressure means 37b and 52 are reduced, and in the region where the tipping moment is large, the axial direction The force of the gas load and the negative pressure by the negative pressure means 37b and 52 can be increased. In this way, the idle operation of the movable scroll 26 is stabilized by switching the action and the stop of the pushing force by the high pressure oil in accordance with the idle angle region of the movable scroll 26.

The invention of claim 10 is similar to the invention of claims 1 and 8, wherein the fixed scroll 22 fixed in the casing 10 and the movable scroll 26 meshing with the fixed scroll 22 are provided. And adjusting mechanisms for adjusting the negative pressure of the movable scroll 26 against the fixed scroll 22 and the negative pressure means 37b and 52 for pushing the movable scroll 26 in the axial direction with respect to the fixed scroll 22 ( It is assumed that a scroll compressor having 67) is provided.

In this scroll compressor, the adjustment mechanism 67 generates a force for pushing the movable scroll 26 out of the fixed scroll 22 against the negative pressure, while compressing the gas during idle of the movable scroll 26. It is characterized in that it is configured to reduce this pushing force in the revolving angle region where the rollover moment acting on the movable scroll 26 becomes equal to or larger than a predetermined value.

In the invention according to claim 10, when the movable scroll 26 revolves to compress gas, the rollover moment acting on the movable scroll 26 varies with the revolution as shown in FIG. When it becomes large in the revolving angle area, the pushing force by the adjustment mechanism 67 is reduced. Therefore, the force of the axial gas load and the pushing force and the negative pressure by the negative pressure means 37b and 52 can be prevented from becoming below the required minimum negative pressure. Except for the angular region, excessive negative pressure is also not generated by operating the movable scroll 26 without reducing the pushing force. In this way, the movable scroll 26 executes a stable idle operation without overturning or overpressure.

According to the invention of claim 11, in the scroll compressor according to claim 10, the adjustment mechanism (67) includes an oil groove (55) formed on the sliding surface of the fixed scroll (22) and the movable scroll (26), An oil introduction passage 53 communicating with the oil groove 55 is provided to introduce the high pressure oil into the oil groove 55, and the oil groove 55 and the oil introduction passage 53 are operated by gas compression. In the revolving angle region in which the rollover moment acting on the scroll 26 becomes equal to or larger than a predetermined value, the communication area is characterized in that the communication area is reduced. For example, when the oil groove 55 is formed in the fixed scroll 22 and the oil introduction passage 53 is formed in the movable scroll 26, the opening end of the oil introduction passage 53 is movable scroll 26. Since the revolution of the circumference of the revolving radius of a circle is a radius, the area of communication with the oil groove 55 is small only in a part of the trajectory (the position of the opening end when the movable scroll 26 is in the revolving angle region). You can lose it.

In the invention according to claim 11, a force for pushing the movable scroll 26 to the fixed scroll 22 is generated when the oil introduction passage 53 communicates with the oil groove 55. On the other hand, in the revolving angle region where the rollover moment acting on the movable scroll 26 by gas compression becomes a predetermined value or more, the communication area is reduced, and the pushing force is reduced. Therefore, in the region where the tipping moment generated by gas compression is small, the force of the axial gas load and the pushing force by the high pressure oil and the negative pressure by the negative-pressure means 37b and 52 are reduced. The force can be reduced to increase the force of the axial gas load, the pushing force by the high pressure oil, and the negative pressure by the negative pressure means 37b, 52. In this way, the idle operation of the movable scroll 26 is stabilized by reducing the pushing force in accordance with the idle angle region of the movable scroll 26.

According to the invention of claim 12, in the scroll compressor according to claim 10, the adjustment mechanism (67) includes an oil groove (55) formed on the sliding surface of the fixed scroll (22) and the movable scroll (26), and An oil introduction passage 53 communicating with the oil groove 55 to introduce the high pressure oil into the oil groove 55, wherein the oil groove 55 is one of the fixed scroll 22 and the movable scroll 26. The oil groove 55 is formed on the other side of the fixed scroll 22 and the movable scroll 26 in a revolving angle region in which the rollover moment acting on the movable scroll 26 by gas compression is equal to or greater than a predetermined value. This low pressure concave portion 71 is characterized in that it is formed.

According to the invention of claim 13, in the scroll compressor according to claim 12, the fixed scroll (22) or the movable scroll (26) such that the low pressure concave portion (71) communicates with a lower pressure space than the inside of the oil groove (55). It is characterized by consisting of a cutout formed in).

In the invention according to claim 12, the operation of moving the oil groove 55 and the low pressure concave portion 71 according to the idle of the movable scroll 26 during the operation of the scroll compressor. Is done. Since the oil groove 55 and the low pressure concave portion 71 are close to the revolving angle region where the rollover moment acting on the movable scroll 26 by gas compression becomes a predetermined value or more, the oil groove 55 High pressure oil can be sent (leaked) to the low pressure concave portion 71. In this case, since the pressure of the oil groove 55 falls, the pushing force is reduced. Therefore, in a configuration in which the movable scroll 26 is usually returned from the fixed scroll 22 to be balanced with the negative pressure, the pushing force can be weakened only in the angular region where the tipping moment is increased. Idle motion is stable.

-effect-

According to the invention of claim 1, the rollover moment is reduced by generating a rollover prevention moment in the revolving angle region where the rollover moment acting on the movable scroll 26 is equal to or greater than a predetermined value. Operation is possible. Therefore, when the overturning moment is increased, the movable scroll 26 can be prevented from being rolled over to prevent the refrigerant from leaking, thereby preventing a decrease in operating efficiency.

In addition, according to the invention of claim 2, the anti-overturning moment acts almost in the opposite direction to the anti-overturning moment in the revolving angle region where the overturning moment acting on the movable scroll 26 becomes equal to or greater than a predetermined value. The action of reducing the rollover moment is made more efficient. Therefore, the idle operation of the movable scroll 26 is more stable, and the fall of operation efficiency can be prevented more reliably.

According to the invention of claim 3, an oil groove 55 is formed in the sliding surfaces of the fixed scroll 22 and the movable scroll 26, and the high pressure oil is introduced into the oil groove 55, By making the point of action of the pressure eccentric from the center of the movable scroll 26, it is possible to reliably generate an anti-overturn moment that reduces the overturning moment, and stabilize the operation of the movable scroll 26.

According to the invention described in claim 4, the above-described action can be generated only by eccentric the annular oil groove 55 from the center of the movable scroll 26, so that the structure can be prevented from being complicated. .

In addition, according to the invention of claim 5, by varying the area of the oil groove 55 on the acting side and the reaction side of the tipping moment with respect to the center of the movable scroll 26, the tipping prevention moment for reducing the tipping moment is reliably generated. You can.

In particular, according to the invention of claim 6, the oil groove 55 has a shape in which part 62 of the overturning moment is cut off with respect to the center of the movable scroll 26. By making the portion 64 of the reaction side of the rollover moment with respect to the center of the rollable scroll 26 wider, the rollover moment is reduced in a simple configuration so that the operation of the movable scroll 26 is stabilized and the operation efficiency of the compressor is increased. Can increase.

Further, according to the invention of claim 8, the overturning moment acting on the movable scroll 26 by gas compression is a pushing force for acting against the negative pressure pushing the movable scroll 26 against the fixed scroll 22. Can be prevented from overturning or underpressure excessive by stabilizing the idle operation of the movable scroll 26 by blocking it in the idle angle region where the predetermined value is equal to or greater than the predetermined value. The fall can be prevented.

According to the invention of claim 9, the oil groove 55 formed on the sliding surfaces of the movable scroll 26 and the fixed scroll 22, and an oil introduction path for supplying high pressure oil to the oil groove 55 ( By appropriately switching the communication state of 53, the idle operation of the movable scroll 26 can be stabilized. For example, when the oil groove 55 is formed in the fixed scroll 22 and the oil introduction passage 53 is formed in the movable scroll 26, the opening end of the oil introduction passage 53 is movable scroll 26. By turning around the circumferential image having a radius of revolution of), the oil introduction passage 53 is a part of the trajectory (the opening end position when the movable scroll 26 is in the revolution angle region). It is easy to make the structure which is not in communication with the groove | channel 55 and communicates in other parts, and the complexity of a structure can also be prevented.

Further, according to the invention of claim 10, the overturning moment acting on the movable scroll 26 by gas compression is a pushing force for acting against the negative pressure pushing the movable scroll 26 against the fixed scroll 22. Can be reduced in the revolving angle range of more than a predetermined value, thereby stabilizing the revolving operation of the movable scroll 26, thereby preventing the occurrence of overturning or negative pressure excess, thereby preventing a decrease in operating efficiency.

According to the invention of claim 11, the oil groove 55 formed on the sliding surfaces of the movable scroll 26 and the fixed scroll 22, and an oil introduction path for supplying high pressure oil to the oil groove 55 ( By appropriately changing the communication state of 53, the idle operation of the movable scroll 26 can be reliably stabilized. For example, when the oil groove 55 is formed in the fixed scroll 22 and the oil introduction passage 53 is formed in the movable scroll 26, the opening end of the oil introduction passage 53 is movable scroll 26. By turning around the circumferential image having a radius of revolution of), the oil introduction passage 53 is a part of the trajectory (the opening end position when the movable scroll 26 is in the revolution angle region). It is easy to communicate with the groove 55 in a small area, and the complexity of a structure can also be prevented.

Further, according to the invention of claim 12, the high pressure oil of the oil groove 55 in the region where the rollover moment acting on the movable scroll 26 by gas compression during the idle operation of the movable scroll 26 becomes equal to or more than a predetermined value. By lowering the pushing force to the low pressure concave portion 71, the revolving operation of the movable scroll 26 can be stabilized and a decrease in operating efficiency can be prevented.

According to the invention described in claim 13, the low pressure concave portion 71 is provided with a cutout portion in the fixed scroll 22 or the movable scroll 26 that communicates with a space having a lower pressure than the inside of the oil groove 55. Thus, the operation of claim 12 can be realized.

First Embodiment

Hereinafter, a first embodiment of the present invention will be described with reference to the drawings. The scroll compressor 1 according to the first embodiment is connected to a refrigerant circuit other than the drawing in which the refrigerant circulates and executes the refrigeration cycle operation, thereby compressing the refrigerant gas.

As shown in FIG. 1, this scroll compressor 1 is provided with the casing 10 comprised from the pressure vessel of a closed dome type. Inside the casing 10, a compression mechanism 15 for compressing refrigerant gas and a compressor motor 16 for driving the compression mechanism 15 are housed. The compressor motor 16 is disposed under the compression mechanism 15. And the compression mechanism 15 and the compressor motor 16 are connected by the drive shaft 17.

The compression mechanism (15) includes a fixed scroll (22), a frame (24) disposed in close contact with the lower surface of the fixed scroll (22), and a movable scroll (26) engaged with the fixed scroll (22). The frame 24 is hermetically bonded to the casing 10 over its perimeter. The casing 10 is divided into a high pressure space 28 below the frame 24 and a low pressure space 29 above the frame 24. The frame 24 includes a frame concave portion 30 concave on the upper surface, a middle concave portion 31 concave on the bottom surface of the frame concave portion 30, and an upper bearing portion protruded to the center of the lower surface of the frame 24. A bearing portion 32 as is formed. The drive shaft 17 is rotatably fitted to the bearing portion 32 via a slide bearing.

The casing 10 is joined to the suction tube 19 for guiding the refrigerant in the refrigerant circuit to the compression mechanism 15 and the discharge tube 20 for discharging the refrigerant in the casing 10 out of the casing 10 in an airtight state. do.

The fixed scroll 22 and the movable scroll 26 have end plates 22a and 26a and spiral wraps 22b and 26b, respectively. In addition, on the lower surface of the plate 26a of the movable scroll 26, a bearing support portion 34, which is located inside the frame recess 30 and the middle recess 31, is connected to the drive shaft 17. do. Outside the bearing portion 34, an annular seal member 36 is disposed so as to be in close contact with the inner peripheral surface of the intermediate recess 31. Inside the frame recess 30 and the middle recess 31, the seal member 36 is pressed against the hard plate 26a of the movable scroll 26 by a biasing means (not shown) such as a leaf spring. The member 36 is partitioned into a first space 37a on the outside and a second space 37b on the inside. In the frame 24, an oil recovery hole (not shown) is provided to allow the refrigeration oil accumulated in the second space 37b to flow out to the bottom of the frame 24, and the second space 37b is formed at the bottom of the frame 24. Communicate with space.

The upper end of the drive shaft 17 is fitted to the bearing portion 34 of the movable scroll 26. On the other hand, the movable scroll 26 is connected to the frame 24 via the Oldham coupling (38), it is configured to revolve in the frame 24 without rotating. The lower surface of the hard plate 22a of the fixed scroll 22 and the upper surface of the hard plate 26a of the movable scroll 26 are sliding surfaces in sliding contact with each other, and the contact portions of the wraps 22b and 26b of the scrolls 22 and 26 are respectively. The clearance gap between the sections is formed as the compression chamber 40. The refrigerant is compressed by the compression chamber 40 shrinking toward the center by the revolution of the movable scroll 26. The refrigerant gas compressed in the compression chamber 40 is discharged below the frame 24 through a discharge passage not shown. As a result, the space below the frame 24 forms the high pressure space 28.

An oil reservoir 48 is formed at the bottom of the casing 10, and an oil supply pump 49 is disposed at the lower end of the drive shaft 17 to pump oil of the oil reservoir 48 by the rotation of the drive shaft 17.

In the drive shaft 17, a drive shaft oil supply passage 51 through which oil pumped up by the oil supply pump 49 flows is formed. In addition, an oil room 52 is formed between the drive shaft 17 and the hard plate 26a in the bearing support 34 of the movable scroll 26, and the oil introduced into the drive shaft oil supply passage 51 is the oil room ( 52) or at each sub oil supply point.

As described above, the high-pressure refrigeration oil is supplied to the oil chamber 52 in the bearing portion 34 of the movable scroll 26, and the second space 37b is filled with the high-pressure refrigerant gas. In the above configuration, negative pressure means 37b and 52 are configured to push the movable scroll 26 to the fixed scroll 22 in the axial direction by using the pressure of the refrigerator oil and the refrigerant gas. Moreover, by pushing the hard plates 22a and 26a of both scrolls 22 and 26 mutually, the sliding surface is comprised as a thrust bearing.

On the other hand, an oil introduction passage 53 extending in the radial direction is formed on the hard plate 26a of the movable scroll 26. The oil introduction passage 53 has an inner end communicating with the oil room 52, and an outer end communicating with an oil groove 55 concave formed on the upper surface of the hard plate 26a. The refrigerator oil is supplied from the oil room 52 to the sliding surface through the oil introduction passage 53. By supplying refrigeration oil to this sliding surface, it is comprised so that the mechanical loss by thrust bearing may be reduced.

The oil groove 55 together with the oil introduction passage 53 constitutes an adjusting mechanism 56 for adjusting the negative pressure of the movable scroll 26 with respect to the fixed scroll 22. The oil groove 55 is formed in the hard plate 26a of the said movable scroll 26, and as shown in FIG. 2, it is formed in ring shape in the outer peripheral side of the wrap 26b. The oil groove 55 is formed at a position where the center is eccentric from the center of the wrap 26b of the movable scroll 26. Specifically, the oil groove 55 has an overturning moment for reducing the overturning moment in the revolving angle region in which the rollover moment acting on the movable scroll 26 becomes greater than or equal to a predetermined value during the movable scroll idle. (See arrow in FIG. 2). For this reason, the oil groove 55 has an operating point of the high pressure pressure on the movable scroll 26 eccentric with respect to the movable scroll 26 toward the reaction side of the tipping moment. As a result, the oil groove 55 has a portion on the overturning moment action side located near the center of the movable scroll 26, and a reaction side portion located away from the center.

Here, the direction in which the rollover moment acts is determined under the following conditions. That is, by the refrigerant gas pressure in the compression chamber 40, the movable scroll 26 receives a radial load as the sum of the axial gas load and the gas force in the direction along the sliding surfaces of the bipolar plates 22a and 26a and the centrifugal force. These loads are maximized at a predetermined crank angle (revolution angle region of the movable scroll 26). Since the rollover moment is generally generated in the acting direction of the radial load at this time, this direction can be determined as the direction in which the rollover moment acts.

As described above, when the oil groove 55 is formed at the position eccentric from the center of the movable scroll 26, the force pushing against the negative pressure of the movable scroll 26 is adjusted to the position eccentric from the center of the movable scroll. Can act reliably as a working point.

The overturning moment is reduced by the overturn prevention moment in the revolving angle region where the pressure of the compression chamber is increased and the overturning moment becomes a predetermined value or more. In the revolving angle region where the compression chamber pressure is low and the rollover moment is smaller than the predetermined value, the rollover prevention moment may be determined from the relation with the negative pressure so that the rollover prevention moment does not become the reverse rollover moment. In this way, when the rollover moment is large and the movable scroll 26 is likely to be rolled over, the rollover can be prevented, and when the rollover moment is small, there is no problem that the rollover moment acts as the rollover moment in the reverse direction. .

As a result, the movable scroll 26 can be always negatively stabilized against the fixed scroll 22, and the idle operation of the movable scroll is stabilized. Therefore, overturning of the movable scroll 26 can be suppressed efficiently and reliably, and the compression efficiency can be reliably improved.

In the first embodiment, since the oil grooves only need to be eccentric from the center of the movable scroll in order to stabilize the operation of the movable scroll, the configuration can be prevented from becoming complicated.

Second Embodiment

In the scroll compressor 1 according to the second embodiment, the adjustment mechanism 56 is different from the first embodiment. Specifically, as shown in FIG. 3, the shape of the oil groove 55 constituting the adjusting mechanism 56 is different from that in the first embodiment. The oil groove 55 has an annular shape concentric with the center of the wrap 26b of the movable scroll 26 and a part of the action side 62 of the roll moment with respect to the center of the movable scroll 26. It forms a disconnected shape. As a result, the oil groove 55 is formed in a substantially C-shaped plane shape.

The oil groove 55 is formed in an arc shape having a predetermined predetermined width. The portion where the groove is not formed in the part of the roll moment acting side 62 of the oil groove 55 is the movable scroll 26 in the revolving angle region where the roll moment acting on the movable scroll 26 is equal to or larger than a predetermined value. The overturning moment is exerted about the center.

Here, the same components as those in the first embodiment will be denoted by the same reference numerals and the description thereof will be omitted.

In this second embodiment, since the oil groove 55 has a flat C-shape, the movable scroll has a working point of the pushing force that the movable scroll 26 receives by the refrigeration oil supply to the oil groove 55 between the sliding surfaces. (26) The center can be eccentrically reliably.

In addition, since the part 62 in which a part of the oil groove 55 is cut off is disposed with respect to the center 59 of the movable scroll 26 in the direction in which the rollover moment acts in the revolving angle region, the high pressure pressure of the refrigerator oil is reduced. The pushing force can be made smaller on the side of the rollover moment and larger on the other side. As a result, the rollover prevention moment for reducing the rollover moment acts in the opposite direction to the rollover moment, so that the rollover of the movable scroll 26 can be suppressed efficiently and reliably, and the compression efficiency can be reliably improved.

Other operations and effects are the same as in the first embodiment.

In this second embodiment, the portion 62 of the oil groove 55 is cut off on the side of the tipping moment, but instead of cutting the portion 62 of the oil groove 55, the width of the portion is changed. You may make area small by narrowing. Even if this occurs, the anti-overturning moment for reducing the overturning moment is generated, and thus the effect similar to the above can be obtained.

Third Embodiment

In the scroll compressor 1 according to the third embodiment, the adjusting mechanism 56 is different from the first and second embodiments. Specifically, as shown in FIG. 4, the shape of the oil groove 55 constituting the adjusting mechanism 56 is different from that in the first and second embodiments.

The oil groove 55 is formed concentrically with the center 59 of the movable scroll 26 on the sliding surface of the movable scroll 26. The oil groove 55 is formed in an annular shape, and an enlarged width portion 64 in which the width of the groove is enlarged is formed in a part of the circumferential direction thereof. The enlarged width portion 64 is located at a position opposite to the direction of action of the tipping moment with respect to the center of the movable scroll 26 in an idle angle region where the tipping moment acting on the movable scroll 26 is equal to or larger than a predetermined value. Is placed.

In this way, since the expanded width portion 64 is formed in the annular oil groove 55 for supplying the oil to the sliding surface, the working point of the pushing force received by the movable scroll 26 by the high pressure of the refrigerator oil on the sliding surface. Can be reliably eccentric from the center of the movable scroll 26.

Since the enlarged width portion 64 of the oil groove 55 is formed with respect to the center 59 of the movable scroll 26 in the direction opposite to the direction of action of the rollover moment in the idle angle region, the center of the movable scroll 26 is formed ( 59, the pushing force on the tipping moment acting side and the pushing force on the reaction side are different, resulting in the tipping moment and the anti-overturning moment in the reverse direction. Therefore, when the overturning moment becomes more than a predetermined value, the overturning moment can be reduced, and the overturning of the movable scroll 26 can be suppressed efficiently and reliably, so that the compression efficiency of the compressor can be reliably improved.

Other configurations, operations and effects are the same as in the first and second embodiments.

Fourth Example

The scroll compressor 1 according to the fourth embodiment shown in FIG. 5 to FIG. 7 has a configuration different from the first to third embodiments in the adjusting mechanism 67. The adjustment mechanism 67 of this fourth embodiment generates a force for pushing the movable scroll 26 back from the fixed scroll 22 against the negative pressure of the negative pressure means 37b, 52, while the refrigerant gas In the revolving angle region in which the rollover moment acting on the movable scroll 26 by compression of the predetermined value is equal to or greater than a predetermined value, the pushing force is interrupted.

The adjusting mechanism 67 includes an oil groove 55 formed in the sliding surface of the fixed scroll 22 and the movable scroll 26, and the oil groove 55 so as to introduce high pressure oil into the oil groove 55. The oil introduction passage 53 which can communicate is provided. The oil groove 55 is formed in an annular shape in the fixed scroll 22, the oil introduction passage 53 is formed in the movable scroll (26). The outer end opening 68 of the oil introduction passage 53 and the oil groove 55 are in a communicating state or a non-communicating state depending on the revolution angle of the movable scroll 26. In other words, the state of communication between the oil groove 55 and the oil introduction passage 53 is changed during the idle scroll 26.

Specifically, the communication state is interrupted in the revolving angle region where the overturn moment acting on the movable scroll 26 by compression of the refrigerant gas is equal to or larger than a predetermined value, and the communication state is maintained in the other regions. As described above, in the present embodiment, since the communication / non-communication between the oil groove 55 and the oil introduction passage 53 is switched, the opening 68 and the oil groove 55 are separately provided to both scrolls 22 and 26. It needs to be formed.

As shown in FIG. 6, the oil groove 55 is provided with an enlarged portion 69 which is enlarged so that the horizontal width thereof protrudes toward the inner circumference. The enlarged portion 69 is formed in an arc shape having a radius of curvature slightly larger than the radius of revolution of the movable scroll 26.

The opening 68 of the oil introduction passage 53 is disposed at a position where communication / non-communication with the enlarged portion 69 of the oil groove 55 of the fixed scroll 22 is repeated. The opening 68 revolves at the position of the enlarged portion 69 of the oil groove 55 in accordance with the revolution of the movable scroll 26, and moves to the outside of the enlarged portion 69 at a predetermined position during the revolution, thereby preventing communication. OFF). The positional relationship between the opening 68 and the enlarged portion 69 of the oil groove 55 is such that the overturn moment acting on the movable scroll 26 by compression of the refrigerant gas during idle of the movable scroll 26 is a predetermined value. The communication is interrupted when the rotational angle region where the force to dissociate the scrolls 22 and 26 is almost attained by the above is almost attained, and the generation of the pushing force by the high pressure oil is stopped. That is, the idle angle region is a region in which the negative pressure of the movable scroll 26 relative to the fixed scroll 22 is relatively increased so as not to overturn the movable scroll 26. In this case, as shown in FIG. And the pushing force due to the discharge of the oil is reduced.

According to the scroll compressor (1) according to the fourth embodiment, the communication between the oil groove (55) and the oil introduction passage (53) is interrupted at a predetermined position during idle, so that the oil supply to the sliding surface is idle during idle. By temporarily stopping, the pushing force acting on the movable scroll 26 by the high pressure oil can be reliably reduced at the predetermined position.

In addition, the pushing force caused by the high pressure oil is reduced in the idle angle region where the tipping moment generated by the compression of the refrigerant gas is almost maximum. Therefore, the axial gas load, the pushing force and the negative pressure means 37b and 52 The force of the negative pressure can be increased. That is, the negative pressure of the movable scroll 26 with respect to the fixed scroll 22 can be reliably maintained above a fixed value. As a result, since the movable scroll 26 can be always negatively stably pressed against the fixed scroll 22, the overturning of the movable scroll 26 can be reliably suppressed, and the compression efficiency can be reliably improved.

Other configurations, operations, and effects are the same as in the first embodiment.

Fifth Embodiment

The scroll compressor 1 according to the fifth embodiment differs from the fourth embodiment in a configuration in which the communication state between the oil groove 55 and the oil introduction passage 53 is changed during idle of the movable scroll 26. As shown in FIG. 8, the communication area between the opening 68 of the oil introduction passage 53 and the oil groove 55 is configured to be reduced at a predetermined position during idle.

That is, in the fourth embodiment, the opening 68 communicates with the oil groove 55 when the revolving moment due to the compression of the refrigerant gas is increased so that the required minimum negative pressure of the movable scroll 26 is increased. In this fifth embodiment, the communication area between the opening 68 and the oil groove 55 is not completely blocked, but the communication area is reduced while maintaining the communication state. .

Therefore, even in this case, the force of the axial gas load by the refrigerant gas and the pushing force by the high pressure oil in the idle angle region can be suppressed from becoming larger than necessary, so that the negative pressure of the movable scroll 26 is kept above a certain value. You can keep it. Thereby, overturning of the movable scroll 26 can be suppressed reliably, and a compression efficiency can be improved reliably.

Other configurations, operations and effects are the same as in the fourth embodiment.

Sixth Example

Unlike the fourth and fifth embodiments, the scroll compressor 1 according to the sixth embodiment has a predetermined rollover moment acting on the movable scroll 26 by compression of the refrigerant gas during idle of the movable scroll 26. In the revolving angle region that is greater than or equal to the value, a portion of the high pressure oil in the oil groove 55 is sent to the low pressure side space in the casing 10.

As shown in FIG. 9, the adjustment mechanism 67 is an oil groove 55 formed in the sliding surface of the fixed scroll 22 and the movable scroll 26, and this oil so that high pressure oil may be introduce | transduced into this oil groove 55. As shown in FIG. An oil introduction passage 53 communicating with the groove 55 is provided. The oil groove 55 and the oil introduction passage 53 are formed in the movable scroll 26. In addition, the fixed scroll 22 has a low pressure concave portion 71 in which the oil groove 55 is adjacent in a revolving angle region in which the rollover moment acting on the movable scroll 26 by compression of the refrigerant gas is equal to or greater than a predetermined value. Is formed.

The low pressure recess 71 is formed by a cutout recessed at the periphery of the sliding surface of the fixed scroll 22 and the movable scroll 26. This cutout part 71 is comprised so that it may communicate with the 1st space 37a of low pressure rather than the inside of the oil groove 55. As shown in FIG. Moreover, this cutout part 71 is comprised so that the oil groove 55 may be closest in the revolving angle area | region where the minimum required negative pressure of the movable scroll 26 by refrigerant gas increases during idle of the movable scroll 26. As shown in FIG. Therefore, when the oil groove 55 of the movable scroll 26 approaches the cut portion 71 of the fixed scroll 22, the sliding contact area between the oil groove 55 and the cut portion 71 becomes small. A portion of the high pressure oil of 55 is leaked to the cutout portion 71 at a lower pressure.

Therefore, in the idle angle region, the pushing force that the movable scroll 26 receives from the oil between the sliding surfaces can be reliably reduced, so that the force with the axial gas load generated by the compression of the refrigerant is no longer necessary. You can stop it from growing. Therefore, by reliably maintaining the negative pressure of the movable scroll 26 with respect to the fixed scroll 22 to a certain value or more, overturning of the movable scroll 26 can be reliably suppressed, so that the compression efficiency can be reliably improved. .

Other configurations, operations and effects are the same as in the fourth and fifth embodiments.

Other Examples

In each of the above embodiments, the high pressure pressure of the refrigeration oil is used to generate the pushing force of the movable scroll 26, but other means may be employed, for example, using the high pressure pressure of the refrigerant gas.

In each of the above embodiments, the high pressure oil in the oil room 52 and the high pressure refrigerant gas in the second space 37b are actuated on the movable scroll 26 to thereby negatively pressurize the movable scroll 26 to the fixed scroll 22. Although a means is comprised, the negative pressure means is not limited to such a structure, You may apply other arbitrary means.

In the first to third embodiments, the overturn prevention moment is generated. In the fourth to sixth embodiments, the pushing force of the high pressure oil is varied, but both of them may be used together.

In the first to third embodiments, the oil groove 55 is formed in the movable scroll 26, but the oil groove 55 may be formed in the fixed scroll 22 instead. In this case, the oil introduction passage 53 can be formed, for example, as passing through the inside of the fixed scroll 22 from the frame 24. In the first embodiment, when the oil groove 55 is formed in the fixed scroll 22, the center of the movable scroll 26 in the revolving angle region at which the overturning moment of the movable scroll 26 is greater than or equal to a predetermined value. What is necessary is just to comprise so that the center of this oil groove 55 may be eccentric. In addition, when the oil groove 55 is formed in the fixed scroll 22 in the second and third embodiments, the center of the oil groove 55 may be formed to coincide with the center of the fixed scroll 22, for example. have.

In the fourth and fifth embodiments, the oil groove 55 is formed in the fixed scroll 22 and the oil introduction passage 53 is formed in the movable scroll 26. However, the oil groove 55 is formed instead. The oil introduction passage 53 may be formed in the movable scroll 26 in the fixed scroll 22, respectively. In other words, the communication between the oil introduction passage 53 and the oil groove 55 may be temporarily interrupted or the communication area may be reduced during the idle scroll 26.

In addition, in the sixth embodiment, the cutout portion 71 is formed in the fixed scroll 22. However, instead of forming the oil groove 55 in the fixed scroll 22, the cutout portion 71 is formed. May be formed on the movable scroll 26. In other words, the cutout 71 and the oil groove 55 may be configured to approach or move away from each other during the idle scroll 26.

As mentioned above, this invention is useful with a scroll compressor.

Claims (13)

Fixed scroll 22 fixed in casing 10, movable scroll 26 engaged with the fixed scroll 22, and negative pressure means for pushing the movable scroll 26 against the fixed scroll 22 in the axial direction. (37b, 52) and the adjustment mechanism 56 for adjusting the negative pressure of the movable scroll (26) relative to the fixed scroll (22), The adjusting mechanism 56 is configured to generate an anti-overturning moment to reduce the overturning moment in the revolving angle region where the overturning moment acting on the movable scroll 26 becomes more than a predetermined value during the idle scroll 26 revolving. Scroll type compressor, characterized in that. The method of claim 1, The adjusting mechanism 56 is configured such that the roll preventing moment acts in a direction substantially opposite to the tipping moment in an idle angle region where the tipping moment acting on the movable scroll 26 becomes equal to or greater than a predetermined value. . The method according to claim 1 or 2, The adjusting mechanism 56 includes an oil groove 55 formed in the sliding surface of the fixed scroll 22 and the movable scroll 26, and an oil introduction passage 53 for introducing high pressure oil into the oil groove 55. , And the oil groove (55) is formed such that the point of action of the high pressure pressure on the movable scroll (26) is eccentric from the center of the movable scroll (26) in the idle angle region. The method of claim 3, wherein The oil groove 55 is formed in the fixed scroll 22 or the movable scroll 26 so that the oil groove 55 is formed in an annular shape and its center is eccentric from the center of the movable scroll 26 in the idle angle region. Scroll compressor. The method of claim 3, wherein The oil groove (55) is a scroll type compressor, characterized in that the area where the hydraulic pressure acts on the acting side of the overturn moment with respect to the center of the movable scroll (26) in the idle angle region is smaller than the reaction side. The method of claim 5, wherein The oil groove 55 is annular concentric with the center of the movable scroll 26, and part 62 of the tip moment acting side is disconnected with respect to the center of the movable scroll 26 in the idle angle region. Scroll compressor. The method of claim 5, wherein The oil groove 55 is an enlarged width portion 64 having an annular concentric shape with the center of the movable scroll 26 and the width of the groove extending toward the reaction of the tipping moment with respect to the center of the movable scroll 26 in the idle angle region. Scroll type compressor, characterized in that having a. Fixed scroll 22 fixed in casing 10, movable scroll 26 engaged with the fixed scroll 22, and negative pressure means for pushing the movable scroll 26 against the fixed scroll 22 in the axial direction. (37b, 52) and an adjustment mechanism (67) for adjusting the negative pressure of the movable scroll (26) with respect to the fixed scroll (22), The adjusting mechanism 67 generates a force for pushing the movable scroll 26 out of the fixed scroll 22 against the negative pressure, while the movable scroll 26 is applied to the movable scroll 26 by gas compression during idle operation of the movable scroll 26. A scroll compressor, characterized in that it is configured to block the pushing force in an idle angle region where an acting overturning moment becomes a predetermined value or more. The method of claim 8, The adjustment mechanism 67 communicates with the oil groove 55 formed in the sliding surface of the fixed scroll 22 and the movable scroll 26, and the oil groove 55 to introduce the high pressure oil into the oil groove 55. Has a possible oil introduction passage 53, The oil groove 55 and the oil introduction passage 53 are configured such that the communication state is interrupted in an idle angle region where the tipping moment acting on the movable scroll 26 by gas compression becomes a predetermined value or more. Scroll compressor. A fixed scroll 22 fixed in the casing 10, a movable scroll 26 engaged with the fixed scroll 22, and a negative pressure means for pushing the movable scroll 26 against the fixed scroll 22 in the axial direction. (37b, 52) and an adjustment mechanism (67) for adjusting the negative pressure of the movable scroll (26) with respect to the fixed scroll (22), The adjusting mechanism 67 generates a force for pushing the movable scroll 26 out of the fixed scroll 22 against the negative pressure, while the movable scroll 26 is applied to the movable scroll 26 by gas compression during idle operation of the movable scroll 26. A scroll compressor, characterized in that for reducing the pushing force in an idle angle region at which the acting overturning moment becomes a predetermined value or more. The method of claim 10, The adjustment mechanism 67 communicates with the oil groove 55 formed in the sliding surface of the fixed scroll 22 and the movable scroll 26, and the oil groove 55 to introduce the high pressure oil into the oil groove 55. Is provided with an oil introduction passage 53, The oil groove 55 and the oil introduction passage 53 are configured to reduce the communication area in an idle angle region where the rollover moment acting on the movable scroll 26 by gas compression becomes a predetermined value or more. Scroll compressor. The method of claim 10, The adjustment mechanism 67 communicates with the oil groove 55 formed in the sliding surface of the fixed scroll 22 and the movable scroll 26, and the oil groove 55 to introduce the high pressure oil into the oil groove 55. Is provided with an oil introduction passage 53, The oil groove 55 is formed in one of the fixed scroll 22 and the movable scroll 26, At the other side of the fixed scroll 22 and the movable scroll 26, the low pressure at which the oil groove 55 is close in the revolving angle region in which the rollover moment acting on the movable scroll 26 by gas compression becomes a predetermined value or more. Scroll type compressor, characterized in that the recess 71 is formed. The method of claim 12, Low pressure concave portion 71, the scroll type compressor, characterized in that composed of the cut portion formed in the fixed scroll (22) or movable scroll (26) so as to communicate with the space of the lower pressure than the oil groove (55).